Escapement for producing intermittent rotary motion of predetermined increments



March 29. 1966 A DOT'TO 3,243,530

ESGAPEMENT FOR PRODUCING INTERMITTENT ROTARY MOTION OF PREDETERMINED INCREMENTS Filed April 10, 1964 3 Sheets-Sheet l INVENTOR. G/ANN/ A. DOTTO ATTORNEY DOTTO I ESCAPEMENT FOR PRODUCING INTERMITTENT ROTARY March 29. 1966 G. A.

MOTION OF PREDETERMINED INCREMENTS 5 Sheets-Sheet 2 Filed April 10, 1964 INVENTOR. GIANN/ A. DOTTO March 29. 1966 G. A DOT 3,243,530

ESOAPEMENT FOR PRODUCING I ERMITTEN'I ROTARY MOTION OF PREDETERMINED INCREMEN'I'S Filed April 10, 1964 5 Sheets-Sheet 3 INVENTOR.

G/ANN/ A. DOTTO ATTORN EYv United States Patent 3,243,530 ESCAPEMENT FOR PRODUCING INTERMITTENT ROTARY MOTION 0F PREDETERMKNED INCRE- MENTS Gianni A. Dotto, Dayton, Ohio,assignor to P. R. Mallory & Co., Inc., Indianapolis, Ind, a corporation of Delaware Filed Apr. 10, 1964, Ser. No. 358,687 11 Claims. (Cl. 200-33) The present invention relates to an escapement, more particularly to escapements imparting timed intermittent or step-by-step snap rotary motion outputs from a substantially constant rotary motion input. Such timed, intermittent rotary motion escapements are employed to periodically actuate control devices such as a switch means that in turn regulates the time sequence of operations embodied in Washing machines and other similar devices.

In a device of this general nature it is desirable that the escapement be actuated aft-er a predetermined interval of time has elapsed. The escapement operates a control device such as a switch means having as a component thereof a series of cam operated switches. The escapement with which the present invention is concerned is of the type having a substantially constant rotary motion input which is translated by the escapement into an intermittent snap rotary motion output. The device would necessarily include a drive motor, a drive gear, an escapement, and a switch means that sequentially actuates a plurality of electric-a1 circuits.

In control timers using escapements, it is desirable that the timer be manually operable to modify the duration or sequence of operation by either shortening certain operations or to skip over them entirely. For this purpose, the timer is provided with a manual operable means coupled to a cam shaft so that an operator is able to modify the duration or sequence of operations in accordance with the desires of the operator.

Several escapements presently available impart intermittent or step-by-step snap rotary motion output from a substantially constant rotary motion input and are used in conjunction with a switch means to form a control timer. These several escapements utilize means for storage of energy during a storage cycle and for subsequently releasing said stored energy during a rel-ease cycle. Generally, the means utilized to store the energy is a coil spring that is either compressed or expanded thus storing energy. When the coil spring is released from its compressed or expanded condition, the energy so stored provides a driving torque for a ratchet wheel and its associated driving means.

The use of an inter-mittent driving means provides the facility of making and breaking switch contacts at a sufficient velocity as to prevent said contacts from being damaged by are over between switch contacts. The intermittent release of stored energy over a relatively short period of time is transferred toa ratchet wheel and then to a cam operated means which controls the sequential operation of a plurality of switch devices.

The present invention provides an intermittent driving means whereby the coil spring and its associated ratchet wheel are replaced by a simple, efficient, inexpensive, accurate, and effective spring biased one-way brake that provides an intermittent driving force which force actuates a cam operated means that in turn controls the sequential operation of a plurality of switch devices.

In addition the present invention provides a novel oneway brake that is capable of locking and releasing a counter-shaft within four minutes of a degree by using a novel seat configuration for a plurality of roller bearings in cooperative relation with substantially V-shaped springs that have a crotch that is substantially three- "ice quarter circular shaped. Several brakes presently available are not capable of locking and releasing a shaft within four minutes of a degree, but are capable of locking and releasing a shaft within only a degree. The inability of such brakes to lock or release within several minutes of a degree introduces appreciable error into the timer control device that cannot be tolerated if optimum timing results are desired.

The novel one-way brake utilizes an odd number of bearings so that no two bearings lie in a single plane that passes through the center of the counter-shaft. If two bearings lie in said same plane, it was found that not only were the bearings subjected to excessive wear, but also the counter-shaft oscillated about its axis introducing additional error into a timer control that cannot be tolerated if optimum results are desired. However, it was discovered by utilizing an odd number of bearings so that no one hearing was positioned in the same plane of another bearing that also passed through the axis of a counter-shaft, the brake was self-centering with respect to the counter-shaft and therefore any oscillation by the counter-shaft was eliminated. It was also discovered that bearing wear was substantially reduced by using an odd number of bearings.

It is an object of the present invention to provide a novel rotary-motion translating means utilized to translate a slow, continuous rotary motion to a rapid, intermittent rotary motion.

A further object of the present invention is to provide an intermittent drive means utilizing a novel one-way brake means associated with a spring bias means.

Still another object of the present invention is to provide an intermittent drive means possessing improved operating characteristics.

Yet another object of the present invention is to provide an escapement means having constant torque advancement characteristics that is also simple to fabricate and assemble.

Still another object of the present invention is to provide a simple, efficient, and practical escapement for timing devices.

A further object of the present invention is to provide an escapement in which each impulse or jump has a precise amount of travel without any over travel.

Yet another object of the present invention is to provide an escapement means for actuating a plurality of multi-contac-t electric switches, said escapement means being inexpensive and accurate and in construction, and more positive in action than preceding escapement means.

Still another object of the present invention is to provide an escapement means associated with a plurality of multi-oontact electrical switches having optimum reliability characteristics aiforded by a construction having a minimum of parts.

The present invention in another of its aspects, relates to novel features of the in-strumentalities of the invention described therein for teaching the principal object of the invention and to the novel principles employed in the instrumentalit-ies whether or not these features and Iprinciples may be used in said object and/or in the said With the aforementioned objects enumerated other objects will be apparent to those persons possessing ordinary skill in the art. Other objects will appear in the following description, appended claims, and appended drawings.- The invention resides in the novel construction, combination, arrangement, and cooperation of elements as here'- inafter described and more particularly as defined" in the appended claims.

The appended drawings illustrate several novel and different embodiments of the present invention and constructed to function in the most advantageous modes devised for the practical application of the basic principals involved in the hereinafter described invention.

In the drawings:

FIGURE 1 is a perspective view of an embodiment of the present invention illustrating the escapement means and associated plurality of sequential switches.

FIGURE 2 is an enlarged perspective view of the present invention particularly illustrating the escapement means associated driven gears, and manually operable means used to modify the sequence of operations of a timer.

FIGURE 3 is an enlarged perspective view of the present invent-ion illustrating in detail the escapement and its location with respect to driving gear and a driven gear.

FIGURE 4 is an enlarged front view illustrating in detail the novel one-way brake.

FIGURE 5 is an enlarged front view of the escapement means showing the movement of said escapement in full and dotted lines respectfully.

FIGURE 6 is an enlarged front view of the escapement illustrating movement of the escapement just prior to and just subsequent to the intermittent movement by the cross hatched counter-shaft illustrated in full and dotted lines respectively.

Generally speaking, the present invention relates to escapements for timing devices through the use of which it is possible to selectively control the sequential operation of a plurality of cam operated switches. Usually, the escapement is coupled between a driving motor means and an intermittently operated cam device. The escapement is utilized for intermittent operation of predetermined plurality of cams which cams in turn operate an associated plurality of switches. A gear reduction means is coupled to said driving means for reduoingthe peripheral velocity of the driving means to a predetermined peripheral speed. An escapement means 'is coupled to the gear reduction means and therefore is used to translate the substantially constant rotary motion output of the driving means to an intermittent rotary motion output of predetermined increments. A gear coupling means is coupled tothe output of the escapement so as to connect the intermittent rotary motion output of the escapement to a switch means.

'IFhe escapement is spring biased by two leaf springs, one situated on each side of a counter-shaft. A oneway brake has a plurality of roller bearings and a spring associated with each of the bearings to urge the bearings to a predetermined position. i A seat for the plurality of roller bearings includes an engagement angle that permits the bearings to be free-wheeling for disengaging in a first direction or clockwise direction and locking or engaging a second direction or counter-clockwise direction. The counter-shaft interfits with the plurality of roller bearings so as to be free-wheeling in a second direction or counter-clockwise direction and to lock with' the plurality of roller hearings in a first direction or clockwise direction. The leaf springs are positioned with respect to the counter-shaft so as to spring bias the countershaft in the first direction until the gear reduction means is rotationally displaced at least 90 degrees in the first direction from an initial position with respect to the counte'r-shaft. Thereafter the leaf springs spring bias the counter-shaft in the second direction and therefore rotationally displace the counter-shaft at least 45 degrees in a second direction or counter-clockwise direction from its initial position. Thus the counter-shaft is not displaced rotationally until the reduction gear means is displaced at least 90 degrees from initial position with respect to the counter-shaft, then the rotational displacement of the counter-shaft is rapid and through an angle at least 45 degrees.

The one-Way brake has a unique seating configuration that is used to seat an odd number of roller bearings and the associated bias springs of said bearings. Each bearfit ing travels in a channel that possesses a progressive engagement angle of eight to ten degrees with respect to a cord of the counter--shaft. The cord of the countershaft is determined by and drawn from the point on said shaft at which the roller bearing locks to said shaft to the point on said shaft at which the roller bearing releases from said shaft. The channel is approximately one and one half times the diameter of the roller hearing so as to provide a channel of ample length to compensate for wear of either the bearing or channel. Spring bias urges the roller bearings to such a position with respect to the channel and with respect to the counter-shaft such that the roller bearings are not required to travel more than four minutes of a degree to either lock or release the counter-shaft. An odd number of roller bearings are utilized so that a plane passing through the axis of any one roller bearing and passing through the axis of the counter-shaft does not pass through the axis of its sister roller bearing. Such placement of the roller bearings allows said hearings to be self-centering with respect to the counter-shaft and the seating configuration of said roller bearings and therefore prevents the countershaft from oscillating. Such placement also maintains equal distribution of the load of the counter-shaft on said bearings thereby reducing bear-ing wear.

Referring now to the drawings, which illustrate the preferred embodiment of the present invention, the drive means is shown in combination with a timer means such as is disclosed in United States Patent No. 2,916,923, issued December 15, 1959, assigned to P. R. Mallory & Company, Inc., the assignee of the present invention. The vital components of the aforementioned timer means includes a driving motor 15 coupled to and spaced from retaining wall 36 of switch means 37 by rivet 6'8 and other rivets not shown. Driving motor 15 is mechanically coupled to rotate a shaft (not shown) of pinion 14 and hence rotate pinion 14 substantially in continuous, rotary motion. Pinion 14 is mechanically coupled or meshed with gear means 13 which includes a reduction gear 12 secured in position by U-shaped mounting bracket 60. Washer 61 is used to longitudinally space reduction gear 12 from U-shaped mounting bracket 60. Counter-shaft 11 projects through aperture 10 centrally positioned in gear 12. Aperture 10 is of sufficient diameter to permit intermittent rotation by counter-shaft 11 yet aperture 10 is of sufficient diameter to provide a means whereby gear 12 is carried by counter-shaft 11. Washer 16 is utilized to longitudinally space large gear 12 from lower support member 19.

Lower support member 19 is utilized to predeterminately space roller 18 and roller 20 from counter: shaft 11. Lower support member 19 is securely coupled to counter-shaft 11 by a centrally located aperture (not shown) in lower support member 19. The major plane of lower support member 19 is perpendicular to the major axis of counter-shaft 11. Upper support member 23 is spaced from and lies in a plane parallel to the plane of lower support member 19. Upper support member 23 is spaced from lower support member 19 by a distance equal to the height of roller 18 and roller 20. Roller 18 and roller 20 are rotatively journalled to upper support member 23 by pins 21 and 22 respectively. Upper support member 23 is coupled to counter-shaft 11 by a centrally located aperture (not shown) in upper support member 23.

Located at a predetermined distance from and equally spaced from the axis of counter-shaft 11 are rollers 18 and 20. The axes of rollers 18 and 20 respectively are parallel to the axis of counter-shaftll and therefore the axes of rollers 18 and 20 are perpendicular to the plane of lower support member 19. Roller 18 and roller 20 are rotatively journalled to lower support member 19 by pins 21 and 22 respectively. Pins 21 and. 22 traverse, rollers 18 and 20 respectively at their axes.

Spring biased one-way brake 42 of the present in vention is of the type whereby counter-shaft 11 is engaged with retaining wall 36 of the switch means 37 when counter-shaft 11 is displaced rotatably in the direction of arrow 62, the clockwise direction. It is obvious that retaining wall 36 is not rotatable, therefore, counter-shaft 11 is maintained in its initial position. Counter-shaft 11 engages retaining wall 36 due to the presence of the coefiicient of friction that exists between the portion of the surface of counter-shaft 11 which engages a first portion of roller bearing 38, and due to the presence of the coefficient of friction that exists between a second portion of roller bearing 38 and a portion of the surface of retaining wall 36 that is adjacent said second portion of roller bearing 38. Retaining Wall 36, roller bearings 38, and counter-shaft 11 are constructed of a steel of suitable hardness, so that any wear particles of steel that might occur cannot subsequently become magnetized thereby adhering to either the said retaining wall, said roller bearings, or said counter-shaft thereby impeding the accurate engaging or disengaging qualities of oneway brake 42. If counter-shaft 11 is chromium plated, no lubricant is needed between the counter-shaft 11 and roller bearings 38; however, if said shaft is not chromium plated, a lubricant is utilized between said counter-shaft and said roller bearings.

Counter-shaft 11 is cylindrical whereas the portion of retaining wall 36 used to seat roller bearings 38 and through which counter-shaft 11 projects at a right angle thereto has a unique configuration 52 utilized to seat at least three roller bearings 38 and an associated plurality springs 39. Each of the plurality of spring 38 is essentially V-shaped except for the crotch portion 64 thereof which is substantially three-quarter circular shaped so as to interfit with a substantially three-quarter circular first portion 53 of configuration 52 adjacent counter-shaft 11.

Ssecond portion 55 of configuration 52 is substantially parallel to a line drawn to bisect a front view of substantially V-shaped spring 39. Leg 65 of substantially V- shaped spring 39 abuts said second portion 55. Ssecond portion 55 maintains leg 65 at a predetermined position with respect to the three-quarter circular crotch portion 64 of spring 39. A flange 66 of said configuration 52 is formed at the point where the first portion 53 and second portion 55 join so as to provide .a pivot point for spring 39 when said spring is compressed or expanded due to the displacement of said bearing 38 toward or away from said spring 39.

A leg 63 of substantially V-shaped spring 39 adjacent roller bearing 38 urges said bearing to a position with respect to counter-shaft 11 and configuration 52 such that bearing 38 is required to traverse the minimum distance of less than four minutes of a degree to either allow counter-shaft 11 to be free-wheeling or to lock said counter-shaft to retaining wall 36. Substantially V-shaped springs 39 are constructed of beryllium copper so that said springs cannot be magnetized and thus accumulate metallic particles causing bearings 38 to skid before engaging counter-shaft 11 or to remain engaged a longer period of time than desired, thus impeding the accuracy of operation of one-way brake 42.

The three-quarter circular first portion 53 of configuration 52 as a second segment terminating in a third portion or channel 54 that provides a seat for roller bearing 39. Channel 54 possesses an engagement angle that is progressively larger with respect to a cord of countershaft 11 drawn between the point on said counter-shaft where said shaft is free wheeling and the point thereon where said shaft is engaged with retaining wall 36. The engagement angle is equal to the angle of the cord of the said shaft plus eight to ten degrees. It has been found that if the engagement angle exceeds the angle of the cord of counter-shaft 11 plus degrees, the counter-shaft will slip before engaging thus impeding the accuracy of the engagement of one-way brake 42 with counter-shaft 11.

6 If the engagement angle is less than the angle of the cord of counter-shaft 11 plus 8 degrees, roller bearings 38 will not disengage properly therefore impeding the accuracy of the disengagement of one-way brake 42 with countershaft 11. Channel 54 is approximately one and one-half times the diameter of roller bearing 38 so as to provide a channel of ample length to compensate for wear of either said bearing or said channel.

A fourth portion 56 of configuration 52 terminates channel 54 substantially on a line that runs through the center of configuration 52. A fifth portion 67 is arcuate and terminates fourth portion 56 a predetermined distance from counter-shaft 11. Fifth portion 67 couples fourth portion 56 to second portion 55. Fifth portion 67 also serves to strengthen channel 54 and second portion 55.

Referring to FIGURE 4 it is apparent from the foregoing disclosure that counter-shaft 11 is free to rotate without engaging retaining wall 36 if said shaft rotates in the counterclockwise direction for the angle of engagement of channel 54 is increasing in the counter-clockwise direction. If counter-shaft 11 rotates in the clockwise direction, said shaft engages retaining wall 36 for the angle of engagement of channel 54 is decreasing in the clockwise direction.

An odd number of roller bearings 38 and associated springs 39 are utilized so that counter-shaft 11 is selfcentering thus eliminating excessive bearing wear caused by counter shaft oscillation, and the tendency of the said shaft to skid on said bearings if said shaft is not centered between said bearings. It was found that if an even number or roller bearings were utilized, a plane drawn through the center of a cross-section of said counter-shaft would also pass through the cross-sectional centers of two of said roller-bearings. If counter-shaft 11 is displaced toward one of said roller bearings, the other said roller bearing lying in a plane passing through its cross sectional center will not he urged downwardly but urged either in the clockwise direction or urged in the counter-clockwise direction depending on the direction in which leg 63 of spring 39 is displaced. The load of said counter-shaft is shifted to the remaining bearings thus appreciably increasing the load on said other bearings and therefore directly increasing wear on said other bearings. Since no support is available to said counter-shaft at the point of separation between said shaft and said bearing, countershaft 11 is free to oscillate thus impeding the accuracy of said one-way brake. However, if at least three roller hearings or any other higher odd number of roller bearings are utilized, no two hearings will lie in a plane drawn through the center of the cross-section of said shaft and through the centers of a cross-section of any two roller bearings. If counter-shaft 11 is displaced toward one roller bearing 38 and therefore away from two other roller bearings 38, leg 63 of spring 39 urge roller bearing 38 in a clockwise direction thus maintaining roller bearing 38 in such a position with respect to channel 54 and countershaft 11 so that said counter-shaft cannot oscillate. It is apparent the load on said bearings remains equally distributed and therefore neither the engaging or disengag ing characteristics of the one-way brake are impeded nor do the roller bearings experience excessive wear.

Elongated leg 25 of Z-shaped leaf spring 24 has a first portion of a face (not shown) that rides on a portion of the periphery of roller 18 and a second portion of said face (not shown) that rides on a portion of the periphery of roller 20. Said face (not shown) of Z-shaped leaf spring 24' is substantially parallel to a plane drawn through the axes of rollers 18 and 20. Therefore, elongated leg 25 substantially traverses a plane drawn tangent to the respective peripheries of rollers 18 and 20. The point at which the elongated leg 25 and stem 30 of Z-shaped leaf spring 24 join is rounded to engage a portion of the periphery of retaining pin 32 and thus Z-shaped leaf spring 24 is maintained in position in a first direction by said retaining pin. Retaining pin 32 is secure to and projects from reduction gear 12 at a right angle thereto. Spaced from retaining pin 32 at substantially a 45 degree angle thereto is second retaining pin 33. Retaining pin 33 is likewise secured to and projects from reduction gear 12 at a right angle thereto. The point at which short leg 26 and stem 30 of Z-shaped leaf spring 24 join is rounded to engage a portion of the periphery of retaining pin 33 and thus Z-shaped leaf spring 24 is held in position in a second direction by said retaining pin.

Elongated leg 28 of Z-shaped leaf spring 27 has a portion of face 59 that rides on a portion of the periphery of roller 18 and a second portion of face 59 that rides on a portion of the periphery of roller 20. Said face 59 of Z-shaped leaf spring 27 is substantially parallel to the axes of rollers 18 and 20.

Elongated leg 28 substantially traverses a plane drawn tangent to the respective peripheries of rollers 18 and 20. The point at which elongated leg 28 and stem 31 of Z shaped leaf spring 27 join is rounded to engage a portion of the periphery of retaining pin 34 and thus Z-shaped leaf spring 27 is maintained in position in a first direction by said retaining pin. Said retaining pin is secured to and projects from reduction gear 12 at a right angle thereto. Spaced from retaining pin 34 at substantially a 45 degree angle thereto is retaining pin 35. Retaining pin 35 like retaining pin 34 is secured to and projects from reduction gear 12 at a right angle thereto. The point at which short leg 29 and stem 31 of Z-shaped leaf spring 27 join is rounded to engage a portion of the periphery of retaining pin 35 and. thus Z-shaped leaf spring 27 is maintained in position in a second direction by said retaining pin. It is seen from the foregoing disclosure that the planes of elongated legs 25 and 28 are substantially parallel to each other. Z-shaped leaf springs 24 and 27 are constructed of any suitable resilient metal.

The distance that separates the axes of either retaining pin 32 or retaining pin 34-v from the axis of counter-shaft 11 is only important in determining the amount of force required to sufliciently displace elongated leg 25 and elongated leg 28 to permit counter-shaft 11 and associated rollers 18 and 20 to snap through an angle of approximately 45 degrees.

Escapement 17 operates in the manner as hereinafter described. Driving motor 15 is coupled to pinion 14 by any suitable means. As hereinbefore disclosed, driving motor 15 is energized so as to rotate pinion 14 at a slow, but substantially constant velocity. The teeth of pinion 14 mesh with the teeth of large gear wheel 12 so as to drive reduction gear 12 at a substantially constant velocity. However, since reduction gear 12 is very much larger than pinion 14, the peripheral speed of reduction gear 12 is substantially less than the peripheral speed of pinion 14. Thus, the interaction of pinion 14 and large gear 12 is such as to reduce the effective rotational speed of driving motor 14. It is understood that the output speed of the driving motor 15 could be any desired velocity depending only on the relationship between circumference of pinion 14 and the circumference of reduction gear 12. In washing machines reduction gear 12 generally has peripheral velocity so as to actuate an escapement means approximately once each minute. It is understood, the peripheral speed of gear 12 could be such that an escapement is actuated any multiple of times per minute or for that matter, any multiple of times per hour.

As discussed previously counter-shaft 11 is centrally located of gear 12 and perpendicular to the axis of gear 12. The face (not shown) of elongated leg 25 of Z-shaped leaf spring 24 rides on one side of rollers 18 and 20-whereas face 59 of elongated leg 28 of leaf spring 27 rides on the opposite side of rollers 18 and 20. As gear 12 is displaced in the direction of arrow 62 or clockwise direction by pinion 14, retaining pins 32, 33, 34 and 35 securely coupled to gear 12 are displaced clockwise. As disclosed hereinbefore leaf spring 24. is maintained in position on gear 12 by pin 32' and pin 33, therefore, leaf spring 24 is likewise displaced in the direction of arrow 62 or clockwise direction. Leaf spring 27 is maintained in position on gear 12 by pin 34 and 35, thus Z-shaped leaf spring 27 is displaced in a clockwise direction by clockwise rotation of gear 12. Rollers 18 and and counter-shaft 11 are situated between parallel faces of elongated arm and elongated arm 28. Rollers 18 and 20 are equally spaced from counter-shaft 11 and are coupled thereto by unitary lower support member 19 and unitary upper support member 23. It is seen that counter-shaft 11 and its associated roller 18 and associated roller 20 would rotate with and in the direction of rotation of gear 12 because of the force exerted on roller 18 and roller 20 by elongated arm 25 and elongated arm 28 in the clockwise direction, but for one-way brake 42 that prevents rotation by counter-shaft 11 and associated rollers 18 and 20 in the clockwise direction.

Adjacent upper support member 23 and parallel thereto is retaining wall 36 of switch means 37. Retaining wall 36 is spaced from upper support member 23 by washer 40 and second end cap 58 of one-way brake 42. Working gear member 41 of counter-shaft 11 projects through an aperture of washer 40 and through the one-way brake 42 to engage gear 43 of switch means 37.

Retaining wall 36 of timer means 37 is coupled to U- shaped mounting bracket by any suitable means such as rivets or screws. U-shaped mounting bracket 60 is utilized to maintain reduction gear 12 in a predetermined position with respect to escapement 17 and driving motor 15.

One-way brake 42 has roller bearings 38 disposed about counter-shaft 11 in such a manner so as to engage and thereafter lock counter-shaft 11 in position when said counter-shaft attempts to rotate in the direction of arrow 52 or clockwise direction. The manner of locking counter-shaft 11 in an initial position when said shaft attempts to rotate in a clockwise direction is described hereinbefore. As a result of locking counter-shaft 11 and its associated rollers in their initial position each of said elements maintains a predetermined position with respect to retaining wall 36 in which one-way brake 42 is seated.

FIGURE 5 illustrates reduction gear 12 rotating in the direction of arrow 62 or the clockwise direction. The initial positions of Z-sh aped leaf spring 24 and of Z- shaped leaf spring 27 are illustrated by solid lines. As gear 12 is rotated in the clockwise direction, counter-shaft 11 and its associated rollers 18 and 20 are maintained in their initial position for one-way bnake 42 prevents clockwise rotation by said countershaft and by said associated rollers. In the intial position, elongated arm 25 and elongated arm 28 each have their respective vertical planes substantially parallel to a continuous vertical plane drawn through the line of the center of roller 18, through the center of counter-shaft 11 and through the center of roller 20. As reduction gear 12 rotates clockwise, the plane of elongated arm 25 and the plane of elongated arm 27 remain substantially parallel, however, said planes are displaced each from the other by rollers 18 and 20 since said rollers are maintained in their initial positions. Elongated arm 25 disengages roller 20, however, said arm continues engagement with roller 18. As elongated arm 25 is further displaced in a clockwise direction, pin 32 moves closer to roller 18 and hence roller 18 traverses elongated a-rm 25 toward pin 32. In so doing, the plane of elongated arm 25 moves through an arc with respect to a continuous plane drawn through the centers of roller 18, of counter-shaft 11, and of roller 20. It is manifest the angle between said two planes in an initial position is zero, however, as reduction gear 12 is rotated the plane of elongate-d arm 25 is displaced angularly from the plane through the centers of rollers 18 and 2t) and counter-shaft 11. As the plane of elongated arm 25 is displaced from its initial position, said arm exerts a force against roller 18 which would cause roller 18 to be displaced in the direction of arrow 62 or clockwise direction. As discussed previously, one-way brake 42 prevents clockwise rota-tion by said counter-shaft and said associated rollers. When the plane of elongated arm 25 forms a 90 degree angle with the plane of centers of rollers 18 and 20 and counter-shaft 11, the force exerted against roller 18 by elongated arm 25 is along the said plane through the centers of rollers 18 and 20 and counter-shaft 11. Hence, the force acts on a neutral position, that is, said force will not act on counter-shaft 11 and its associated rollers 18 and 20 either in the clockwise direction or in the counterclockwise direction for said force is acting along the axis of counter-shaft 11 and associated rollers 18 and 20. As elongated arm 25 is further rotated, it forms an angle that is greater than 90 degrees with said plane through the centers of rollers 18 and 20 and counter-shaft 11, thus the force exerted against roller 18 by elongated arm 25 is no longer such that said force tends to displace said roller in the clockwise direction, but rather the force exerted against roller 18 by elongated arm 25 acts to displace said roller in the direction of arrow 69 or counter-clockwise direction. As discussed previously counter-shaft 11 is free to rotate in the counter-clockwise direction, hence elongated spring arm 25 displaces counter-shaft 11 in a counter-clockwise direction with a rapid snap rotary motion that is associated with escapements.

Elongated arm 28 assumes the position with respect to roller 18 and 20 that elongated arm 25 had occupied and elongated arm 25 assumes the position with respect to rollers 18 and 20 that elongated arm 28 had occupied. The operational relationship between elongated arm 28 and rollers 18 and 20 and the operational relationship between elongated arm 28 and roller 28 is essentially the same as disclosed in conjunction with the disclosure of the interaction between elongated arm 25 and rollers 18 and 20 and elongated arm 25 and roller 18,

When the angle between the plane centers of countershaft 11 and rollers 18 and 20 and the plane of elongated arm 25 and the angle between the plane through the centers of countershaft 11 and rollers 18 and 20 and the plane of elongated arm 28 are greater than 90 degrees, elongated arm 25 exerts a force in the direction of arrow 69 or counter-clockwise direction against roller 18 and elongated arm 28 exerts a force in the direction of arrow 69 or counter-clockwise direction against roller 20 so as to displace counter-shaft 11 and said associated rollers 18 and 20 in a counterclockwise direction. The angle between said plane through the centers and the plane of elongated arm 25 and between said plane through the centers and the plane of elongated arm 28 increases until the angle between said plane through the centers and the plane of elongated arm 25 and the angle between said plane through the centers and the plane of elongated arm 28 are respectively 180 degrees. In such a position said plane of centers and the planes of the respective elongated arms 25 and 28 are substantially parallel. Countershaft 11 and associated rollers 18 and 20 are displaced in the direction of arrow 69 or counter-clockwise direction from their respective initial positions by approximately 45 degrees. It is manifest the second and subsequent intermittent snaps of escapement 17 occur in substantially the same manner as disclosed hereinabove. It is understood escapement 17 will produce intermittent snaps and thus intermittent displacement of counter-shaft 11 in the counter-clockwise directionso long as drive means functions.

A counter-clockwise rotation of 45 degrees is the minimum amount intermittent displacement of counter-shaft 11. The distance between the axes of counter-shaft 11 and rollers 18 and respectively will influence the amount of intermittent displacement of counter-shaft 11. The greater the distance between said axes, the more nearly the displacement of counter-shaft 11 will approximate 45 degrees. The angle between a line drawn from the axis of counter-shaft 11 to the axis of associate roller 18 or to the axis of associated roller 20 and a line drawn 10 from'the axis of counter-shaft 11 to a point tangent to the outer periphery of either roller 18 or roller 20 is the number of degrees in excess of 45 degrees that counter-shaft 11 will be displaced in the counter-clockwise direction.

It is noted therefore, that escapement 42 will be actuated approximately eight times per revolution of reduction gear 12. Theoretically, counter-shaft 11 will be displaced counter-clockwise 45 degrees, but as disclosed hereinbefore the counter-clockwise displacement is influenced by the distance between the axis of roller 18 and the axis of counter-shaft 11 and the diameter of roller 18. Roller 18 is used as an example herein inasmuch as the spacing of roller 20 from counter-shaft 11 and the diameter of roller 20 is identical to that of roller 18.

The intermittent movement of counter-shaft 11 is transferred to gear 43 of switch means 37 by means of working gear member 41 of counter-shaft 11 meshing with gear 43.

Intermittent movement by working gear member 41 in the counter-clockwise direction causes displacement of gear 43 in the clockwise direction.

One-way brake 44 is similar in structure and similar in function to that of one-way brake 42 described hereinbefore. One-way brake 44 differs in that said one-way clutch engages when rotated in a clockwise direction whereas one-way brake 42 engages when rotated in the counter-clockwise direction and differs in that one-way brake 44 disengages when rotated in the counter-clockwise direction whereas one-way brake 42 disengages when rotated in the clockwise direction. The components comprising one-way brake 44 are substantially the same as the elements comprising one-way clutch 42 except that the components of one-way brake 44 are positioned to engage shaft 45 if said shaft attempts to rotate in the counterclockwise direction. Accordingly the components of one-way brake 44 are denoted by the same numerals that denoted the components of one-way brake 42 except that said numerals are primed to avoid confusion with one-way brake 42.

Working gear member 41 intermittently displaces gear 43 in the clockwise direction thus engaging gear 43 to shaft 45 through the medium of one-way brake 44. Shaft 45 is displaced intermittently in the clockwise direction by the intermittent displacement of counter-shaft 11. Shaft 45 has coupled thereto a plurality of earns 46 which are constructed to actuate a plurality switch means 48 for each intermittent movement by counter-shaft 11 of escapement 17.

Coupled to shaft 45 and at a right angle thereto is spring arm 47 of detent means 49. Gear 43 has a continuous plurality of raised projections 50 that engage spring arm 47. Raised projections 50 are located between the outer periphery of gear 43 and the axis of gear 43. Raised projections 50 are radially placed on gear 43 and are parallel to the axis of said gear. Spring arm 47 is displaced in the clockwise direction by rotation of shaft 45 in the clockwise direction. A clockwise direction of rotation allows shaft 45 to be free-wheeling in one-way brake 44. Extremity 51 of spring arm 47 engages projections 50. In each instance when extremity 51 rides over a particular projection 50, spring arm 47 emits an audible click denoting a particular position of the plurality cams 46 coupled to shaft 45 with respect to the plurality of switch means 48. Thus the cooperation between spring arm 47 and projection 50 permits the effective external indexing of shaft 50 by manually rotating knob 61 coupled to shaft 45. That is, any operator knowing the initial position of shaft 45, the said operator could count the number of audible clicks to locate shaft 45 at a second known index position and hence start timer means 37 at a position, that modifies the duration or sequence of operations in accordance with the desires of the operator.

While the invention is illustrated and described in its preferred embodiment, it will be understood that modifications and variations may be effected without departing from the scope of the novel concepts of this invention as :sets forth in the appended claims.

Having thus described my invention, I claim:

1. A timer means comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction means coupled to said driving means for reducing said rotary motion output of said driving means to a predetermined rotary speed; a leaf spring biased escapement coupled to and driven by said driving means, said escapement including: a one-way means carried by a shaft that is free wheeling of said shaft in a first direction and locked with said shaft in a second direction for trans lating said substantially constant rotary motion output of said driving means to an intermittent rotary motion output of predetermined increments; a switch means having a plurality of electrical circuits that are sequentially actuated as a result of said intermittent rotary motion output of said leaf spring biased escapement; and a gear coupling means coupled to said output of said leaf spring biased escapement to couple said intermittent rotary motion output of said leaf spring biased escapement to said switch means.

2. Means for producing intermittent rotary motion of predetermined increments comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction meanscoupled to said driving means for reducing said rotary motion output of said driving means to a predetermined speed; a leaf spring biased escapement coupled to and driven by said gear reduction means, said escapement including: a one-way brake that is free wheeling in a first direction and locked in a second direction; two leaf springs securely fixed to a face of said gear reduction means; and a counter-shaft with associated rollers positioned on opposite sides of said counter-shaft and coupled thereto by a support means, said leaf springs positioned so as to spring bias said counter-shaft and said associated rollers and thereby prevent rotation by said counter-shaft and said associated rollers until said reduction gear is rotationally displaced a predetermined increment in a first direction from an initial position with respect to said counter-shaft and said associated rollers, thereafter said counter-shaft and said associated rollers are rotationally displaced in a second direction through a predetermined arc.

3. A means forproducing intermittent rotary motion of predetermined increments, as set forth in claim 2 wherein said counter-shaft and associated rollers are dis placed at least 45 degrees in a second direction after at least a 90 degree displacement by said gear reduction means in a first direction.

4. A means for producing intermittent rotary motion of predetermined increments, as set forth in claim 2 wherein said one-way brake includes: at least three roller bearings; a spring associated with each of said roller bearings to urge said hearings to a predetermined position; a seat for said roller bearings wherein said seat includes an engagement angle that permits said bearings to be free wheeling in a first direction with respect to said counter-shaft and lock in a second direction with respect to said counter-shaft.

5. Timer control means comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction means coupled to said driving means for reducing said rotary motion output of said driving means to a predetermined rotary speed; a leaf spring biased escapement for translating said substantially constant rotary motion output of said driving means to an intermittent rotary motion output of predetermined increments including a one-way brake comprising: a plurality of roller bearings; a spring adjacent each of said plurality of roller hearings to urge said hearings to a predetermined position; and a seat for said plurality of roller'bearings wherein said seat includes an engagement angle that permits said plurality of roller hearings to be free wheeling in a first direction and locking in a second direction.

6. Timer control means comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction means coupled to said driving means for reducing said rotary motion output of said driving means to a predetermined rotary speed; a leaf spring biased escapement that is displaced at least 45 degrees in a first direction after at least a degree displacement by said gear reduction means in a second direction said leaf spring biased escapement comprising: a one-way brake including a plurality of roller bearings that are free wheeling in a first direction and locking in a second direction; a spring adjacent each of said roller hearings to urge said bearings to a predetermined position; a seat for said plurality of roller bearings wherein said seat includes an engagement angle that permits said bearings to be free wheeling in a first direction and locking in a second direction; two leaf springs securely fixed to a face of said gearreduction means; a counter-shaft interfitting with said plurality roller bearings so as to be free wheeling in a second direction and to lock with said plurality of roller bearings in a first direction; said leaf springs biasing said countershaft in a first direction until said reduction gear means is rotationally displaced at least 90 degrees in said first direction from an initial position with respect to said counter-shaft, thereafter said leaf spring biasing said counter shaft in said second direction rotationally displacing sa id counter-shaft in said second direction at least 45 degrees from said initial position; a switch means having a plurality of switches that are sequentially actuated as a result of said intermittent rotary motion of said counter-shaft; and a gear coupling means coupled to the output of said counter-shaft to couple the intermittent rotary motion output of said counter-shaft to said switch means.

7. A timer means comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction means coupled to said driving means for reducing said rotary motion output of said driving means to a predetermined rotary speed; a leaf spring biased escapement coupled to and driven by said driving means, said escapement including a one-way brake for translating said substantially constant rotary motion output of said driving means to an intermittent rotary motion output of predetermined increments wherein said one-way brake is free wheeling in a first direction and locked in a second direction, two leaf springs fixed to a face of said gear reduction means, and a counter-shaft and associated rollers positioned on opposite sides of said counter-shaft and coupled thereto by a support means, the plane of said leaf springs being parallel to the plane of axes of said counter-shaft and said associated rollers for a predetermined interval of time first direction and thereafter to spring bias said counter-shaft and said associated rollers in said second direction; a switch means having a plurality of electrical circuits that are sequentially actuated as a result of said intermittent rotary motion output of said leaf spring biased escapement; and a gear coupling means coupled to said output of said leaf spring biased escapement couple said intermittent rotary motion output of said leaf spring biased escapement to said switch means.

8. A one-way brake positioned on a shaft comprising: a plurality of roller bearings; a substantially V-shaped spring adjacent each of saidplurality of roller hearings to urge said hearings to a predetermined position; and a seat for said plurality of roller bearings wherein said seat includes an engagement angle that permits said plurality of roller bearings to be free-wheeling in a first direction and locking in a second direction, said engagement angle is equal to the angle of a cord of said shaft as determined by the point thereon where said shaft is free-Wheeling and the point thereon where said shaft is engaged with said brake plus 8 to 10 degrees.

9. A one-way brake positioned on a shaft as set forth in claim 8, wherein said plurality of bearings include an odd number thereof equally spaced about said shaft so as to be self-centering with respect to said shaft.

10. Means for producing intermittent rotary motion of predetermined increments comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction means coupled to said driving means for reducing said rotary motion output of said driving means to a predetermined speed; a leaf spring biased escapement coupled to and driven by said gear reduction means, said escapement including a one-way brake carried by a counter-shaft that is free wheeling of said countershaft in a first direction and locked with said countershaft in a second direction, a plurality of leaf springs securely fixed to a face of said gear reduction means, roller positioned about said counter-shaft and coupled thereto by a support means, said leaf springs biasing said countershaft and said rollers thereby preventing rotation by said counter-shaft and said rollers until said reduction gear is rotationally displaced a predetermined increment in a first direction from an initial position with respect to said counter-shaft and said rollers, thereafter said countershaft and said associated rollers are rotationally displaced in a second direction through a predetermined arc.

11. Means for producing intermittent rotary motion of predetermined increments comprising: a driving means for producing a substantially constant rotary motion output; a gear reduction means coupled to said driving means for reducing said rotary motion output of said driving means to a predetermined speed; a leaf spring biased escapement coupled to and driven by said gear reduction means, said escapement including a one-way brake carried by a counter-shaft that is free Wheeling of said counter-shaft in a first direction and locked with said counter-shaft in a second direction, a plurality of leaf springs securely fixed to a face of said gear reduction means, rollers positioned on opposite sides of said counter-shaft and coupled thereto by a support means, said leaf springs biasing said counter-shaft and said rollers thereby preventing rotation by said counter-shaft and said rollers until said reduction gear is rotationally displaced a predetermined increment in a first direction from an initial position with respect to said counter-shaft and said rollers, said leaf springs storing energy as said reduction gear is displaced through said predetermined increment, thereafter said countershaft and said associated rollers are rotationally displaced in a second direction through a predetermined are by release of said stored energy of said leaf springs.

References Cited by the Examiner UNITED STATES PATENTS 2,391,718 12/1945 Lindemann 20038 X 2,874,238 2/1959 Jackson 200 X 2,916,923 12/1959 Smith et a1 74152 X 3,188,409 6/ 1965 Linn 200 -38 BERNARD A. GILHEANY, Primary Examiner.

G, MAIER, Assistant Examiner. 

1. A TIMER MEANS COMPRISING: A DRIVING MEANS FOR PRODUCING A SUBSTANTIALLY CONSTANT ROTARY MOTION OUTPUT; A GEAR REDUCTION MEANS COUPLED ROTARY MOTION OUTPUT; REDUCING SAID ROTARY MOTION OUTPUT OF SAID DRIVING MEANS TO A PREDETERMINED ROTARY SPEED; A LEAF SPRING BIASED ESCAPEMENT COUPLED TO AND DRIVEN BY SAID DRIVING MEANS, SAID ESCAPEMENT INCLUDING: A ONE-WAY MEANS CARRIED BY A SHAFT THAT IS FREE WHEELING OF SAID SHAFT IN A FIRST DIRECTION AND LOCKED WITH SAID SHAFT IN A SECOND DIRECTION FOR TRANSLATING AND SUBSTANTIALLY CONSTANT ROTARY MOTION OUTPUT OF SAID DRIVING MEANS TO AN INTERMITTENT ROTARY MOTION OUTPUT OF PREDETERMINED INCREMENTS; A SWITCH MEANS HAVING A PLURALITY OF ELECTRICAL CIRCUITS THAT ARE SEQUENTIALLY ACTU- 